Micro-feed adjusting mechanism



April 1956 B. E. BARINGER ETAL 3,244,023

MICRO-FEED ADJUSTING MECHANISM 3 Sheets-Sheet 1 Filed June 1. 1964 MARVIN A. HOLE JOHN A. HUBER April 195-6 E. E. BARINGER ETAL 3,244,023

MICRO-FEED ADJUSTING MECHANISM Filed June 1, 1964 3 Sheets-Sheet 2 BERLYN E BAR/N65,? MARVl/V A. HOLE JOHN A. HUBER April 5, 1966 B. E. BARINGER ETAL 3,244,023

MICRO-FEED ADJUSTING MECHANISM 3 Sheets-Sheet 5 Filed June 1, 1964 J y m M W M Rum T A T Z MT A 54H W L VN mm BMw v! 5 United States Patent Ofiice 3,244,023 Patented Apr. 5, 1966 3,244,023 MICRO-FEED ADJUSTING MECHANISM Berlyn E. Baringer and Marvin A. Hole, Livonia, and

John A. Huber, Birmingham, Mich., assignors to Coilfeed Systems, Inc., Detroit, Mich, a corporation of Michigan Filed June 1, 1964, Ser. No. 371,270 18 Claims. (Cl. 74-600) This invention relates to metal strip feeding devices, and more particularly to metal strip feeding devices of the reciprocating rack type in which the mechanism feeds a predetermined but adjustable length of strip to another apparatus.

Micro-feed adjusting mechanisms are well known in the art. One example of the prior art is disclosed in Budlong Patent No. 3,090,250 in which a metal st-rip feeding device of the reciprocating rack type is controlled by means of a crank arm and an eccentric mounted on the crank arm to manually adjust the length of the strip fed by the device. The prior art devices, however, exhibit certain disadvantages. For example, they include provisions for adjusting the length of the strip being fed only while the strip feed apparatus is in operation. Alternatively, other devices contain provision for adjusting the length of the strip material being fed only when the strip feed apparatus is stopped. Further, certain of these devices include provisions for adjusting the length of the strip being fed in which equal adjustments or degrees of angular rotation of a manually operated crank arm produce difierent degrees of change in the length of the strip being fed. Stated in another manner, certain of the prior art devices employ a manually operable handle for controlling this length of the strip, and the handle is coupled through a mechanism in which a substantially non-linear relationship exists between the degree of rotation of the handle and the degree of change of the length of the strip. Accordingly, it is an object of this invention to provide an improved microfeed adjusting mechanism.

It is another object of this invention to provide a feed adjusting mechanism for a strip feeding apparatus in which the length of the strip can be quickly and accurately adjusted either while the apparatus is in operation or while the apparatus is stopped.

A further object of this invention is to provide a microfeed adjusting mechanism for a strip feed apparatus in which a substantially linear relationship exists between the degree of movement of a manually controllable member and the degree of movement of the length of the strip being fed by the apparatus.

A still further object of this invention is to provide an apparatus for adjusting the length of a strip being fed from a strip feeding device which apparatus may be quickly and accurately adjusted to a high degree of precision and may be adjusted either during the operation of the strip feeding device or while the strip feeding device is stopped.

A still further Object of this invention is to provide a strip feeding apparatus with an adjustable mechanism including a manually operable crank in which the amount of adjustment of the strip is the same for each increment of rotation of the crank. In other words, no matter how far the adjustment is made, the amount of adjustment is substantially always the same amount for each revolution of the crank.

Briefly, in accordance with aspects of this invention, we have discovered an improved device for adjusting the stroke of a rack relative to a trunnion by employing a first gear rotatably mounted on the trunnion and having an eccentric surface depending therefrom, a second gear secured to the trunnion, a rack rotatably engaging the eccentric surface, means coupling the first and second gears,

and means mounted on the rack for varying the position of said first gear relative to said second gear. In accordance with one illustrative embodiment, this coupling means includes a universal coupling and a bevel gear train, and the position varying means includes means for manually adjusting one of the bevel gears of the bevel gear train to position this one bevel gear and while so doing to position the eccentric. Preferably, the eccentric surface is generated by producing a cylindrical hole eccentrically in a cylindrical member which couples a trunnion to a rack, such that the change in the rack stroke varies in a substantially linear manner with the angular change in the position of the eccentric surface relative to the trunnion.

In accordance with still other aspects of this invention, We employ a coupling and a. bevel gear train in which one of the gears is mounted on a shaft pivotally mounted on the rack and in which a linking arrangement including a square rod is employed to link the pivotally mounted gear shaft to a manually operable handle wherein the position of the pivotally mounted shaft and the position of the eccentric may be modified either while the rack is reciprocating or while the rack is stationary.

in accordance with other aspects of this invention, we have discovered an apparatus for modifying the stroke of a rack relative to a crank arm which apparatus includes a first gear rotatably eccentrically mounted on the trunnion of the crank arm, an eccentric member integral with the first gear and having an external eccentric surface, a second gear secured to said trunnion, a bevel gear train rotatably mounted on said rack and operatively connected to said first gear, an Oldham coupling for coupling said second gear to said bevel gear train, said bevel gear train including a gear shaft pivotally mounted relative to the rack and means for positioning the pivotally mounted shaft relative to said rack whereby changes in position of said pivotally mounted shaft are accompanied by proportionate rotation of said first gear and proportionate rotations of said eccentric member. Advantageously, this eccentric surface is gene-rated by producing a cylindrical passage eccentrically through a cylindrical member whereby the changes in the stroke of said rack vary in a substantially linear manner with the changes in position of said pivotally mounted gear shaft. Also advantageously, this means for positioning the pivotally mounted shaft includes a link coupled to the shaft, a threaded rod, a slide threadably engaging the threaded rod and coupled to the link, a square rod operatively connected to the threaded rod and means slidably engaging the rod for rotating the rod such that the threaded rod may be rotated to pivot the shaft while the rack is stationary, or while the rack is reciprocated thus to change the stroke of the rack either while the apparatus is stationary or while the apparatus is in motion.

These and various objects and features of the invention will be more clearly understood from a reading of the detailed description of the invention in conjunction with the drawings in which:

FIG. 1 is a side elevational view of a punch press equipped with the adjustable crank mechanism of the invention and which is illustrated in combination with feeding rolls for the press, the same being intermittently actuated by a rack and pinion mechanism;

FIG. 2 is a view in elevation, partly in section, taken along the lines 2-2 of FIG. 1;

FIG. 3 is a view in elevation of a throw block constituting a portion of the invention;

FIG. 4 is a bottom plan view of the throw block of FIG. 3;

FIG. 5 is a view in elevation, partly in section, of the device of FIG. 2, taken along the line 55 thereof and looking in the direction of the arrows;

then in a counter-clockwise direction.

FIG. 6 is a view in elevation and in section of the device of FIG. 2, taken along the line 6-6 thereof and looking in the direction of the arrows; and,

FIG. 7 is a view in section, taken along the line 7-7 of FIG. 6.

Referring now to the drawings in which like numbers are employed to designate the same parts and particularly to FIGS. 1 and 2, the punch press selected for illustrating the present invention includes a pair of welded or cast uprights such as 28, which are preferably suitably spaced to position a bed plate between the uprights and which additionally mount a vertically reciprocating plunger for coacting with a bed plate, all of which constitutes conventional structure. The plunger is actuated by a main operating shaft 21, shown in FIG. 2, disposed transversely of the press and journaled for rotation in the uprights, such as 20. Upon rotation of the main operating shaft 21 the plunger is reciprocated vertically and thus the plunger and die carried thereby will have movement to and from the bed plate of the press to perform the desired punching, cutting or forming operation on the stock material being fed thereto. The feeding of the strip material to the punch press takes place intermittently in timed relation with the reciprocating movements of the plunger actuated die. For the feeding operation the press may be equipped with feeding rolls on either one or both sides thereof, or on either one or both ends thereof. The feeding rolls may also be self contained in a separatehousing. However, for disclosing the micro-feed adjusting device of the invention and the crank arm and reciprocating rack associated therewith, only the feed rolls at the entrance end are illustrated and, accordingly, the description is limited thereto.

The bracket 22 extending laterally from the upright on the feeding side of the press provides the support for the feed rolls 23, 24. The rolls 23, 24 are joumaled by a pair of side members 25, 26 which are securely fastened at their base to the bracket 22. A shaft 27 rotatably supporting the top roll 23 extends a short distance beyond to project on each side of its journaling member, and this relationship is also true of a shaft 28 for the bottom roller 24. The left hand end, as viewed in FIG. 1, of the shaft 28 is reduced in diameter and extends a sufficient distance to enter a rack and pinion housing 30'for operative connection with driving elements located within the housing. The right hand end of rolls 23, 24 are each normally provided with a gear as 27a, 28a, and which have meshing relation so that the rolls will rotate in unison and to a like extent. Also, the top roll 23 may be provided with suitable means (not shown) for releasing and lifting the top roll to facilitate the insertion of stock material between the rolls 23, 24.

The housing 30 journals a shaft 32 to which is fixed a gear 33. The gear has meshing relation with a linear set of teeth 34 of a reciprocating rack 35. The operative end of the rack 35 is received and guided by the housing 30 and thus as the rack reciprocates, the gear 33 and the shaft 32 in a feeding direction only is transmitted to shaft By means of a conventional one-way clutch mounted on the shaft 32 and combined with interconnecting gearing, all of which is located within a separate housing 3911, the rotation of the shaft 32 is in feeding direction only is transmitted to shaft 28 of the lower feed roll.

In order that the adjustable crank mechanism can be actuated during operation of the press, it is necessary to provide a suitable adjustment means such as a handwheel 36 for effecting these adjustments. It will be understood that this adjustment function may also be carried out by a suitable motor means. The handwheel 36 is conveniently located for access bythe operator, and in this particular embodiment is mounted on bracket 22 by suitable means, such as by a group of bolts 37. A flexible drive 38 operatively connects the handwheel with a gear 4% located within and .journaled by a bracket housing 41.

The housing 41 is suitably fixed to the reciprocating rack or crank arm 35 on the side opposite the teeth 34 and thus the bracket has movement with the rack. The housing 41 also journals a pinion shaft 42 having a pinion 43 fixed thereto and meshes with the gear 40. Rotation of the handwheel 36 is thus imparted to the pinion shaft 42 and to a splined tube 44 which is fixed to the upper extending end of the pinion shaft. The upper end of the splined tube 44 is suitably journaled by a bracket 45 which is anchored on the reciprocating rack, and this end is provided with a square shaped opening for receiving a square rod 46. The rod 46 extends for approximately the length of the rack so as to have connection at its upper end with the adjustable crank mechanism for adjusting the relative position of an eccentric member relative to a shaft on the throw block, all of which will be subsequently described.

As best seen in FIG. 2, the main operating shaft 21 acts as a drive shaft for the micro-feed adjusting mechanism and the rack. The drive shaft 21 is shown as being adjustably mounted to the throw block 48 but it will be understood that, if desired, the drivershaft 21 maybe fixedly connected to the throw block48 by any suitable means. As best seen in FIG. 2 the drive shaft 21 is drivably connected to the hub 49a by means of the key 49. The hub 49a has an enlarged annular portion which is seated in the annular recess 48a formed in the throw block 48. The enlarged annular portion of the hub 49a is adapted to be adjustably connected to the throw block 48 by means of a plurality of suitable bolts 48b-which pass through the arcuate slots 4% and are threadably engaged in the throw block 48. A T-bolt or trunnion 50 which has a dovetail T-portion 51 is slidably mounted in a complimentary channel 52 in the throw block 48 and threadably engages a screw 53. The rack 35 is rotatably mounted on the T-bolt 50 by means of a drive sleeve 54, an ecentric 55 and bearings 56, 57. The eccentric 55 is formed integrally with a gear 58, and the eccentric 55 and gear 58, are a portion of the means for micro adjustment of the strip feed mechanism. Eccentric 55 includes an eccentric surface 59 which is eccentric to the periphery of the T-bolt 50 and is also eccentric to the inside diameter of the gear 58. The inside diameter or bore of the gear 58 is eccentric to the outside diameter or the teeth of the gear and the degrees of eccentricity of the gear teeth of gear 58 and of the surface 59 are the same. That is, the gear 58 and surface 59 are concentric. A circular gear 60 is rotatably mounted on a pin 61 secured to the rack 35 such that the gears 58, 60 are always enmeshed. Eccentric gear 58 is rotatably mounted on the trunnion 50 by means of bearings 57 and 62. The gears 58, 60 are in continued meshed relationship because the rack 35 rides on the eccentric surface 59. A gear train and universal coupling couples the rotation of the trunnion 5G to the gear 58. All the gears of this gear train have a predetermined teeth relationship such that the eccentric gear 58 makes one revolution for each revolution of the throw block 48 and the trunnion 50 and this in turn is controlled by a drive gear 64 which is keyed to the trunion 50 by means of a suitable key or spline 65. The key or spline 65 engages a suitable axially extending slot, not shown, in gear 64 which slot permits the gear 64 to slide axially relatively to the trunnion St). A plate 67 is rotatably mounted on trunnion 5! by means of bearings 68. The left hand bearing 68, as viewed in FIG. 2, is spaced from the hearing 62 by means of a washer 69. The gear 64 is retained on trunnion 50 by means of a nut 70 which threadably engages a threaded portion 71 of trunnion 50. Gear '64 The stroke of the rack 35 is determined primarily by i the length of the crank arm measured between the axes of the main drive shaft 21 and the trunnion 50. As best seen in FIGS. 2, 3 and 4, this distance may be adjusted by releasing nut 70, and rotating the extension 77 of screw 53 in an appropriate direction. Because the screw 53 is rotatably mounted in collar 76 and is journalled in a sleeve 78 and a pair of bearings 79 and threadably engages dovetail 51 of trunnion 50, rotation of screw 53 constitutes a coarse adjustment of the length of the crank arm. The collar 76 is secured to the throw block 48 by any suitable means, as by the bolts 76a. After this coarse adjustment, nut 70 is tightened to apply an axial force through gear 64, washer 72, the outer bearing 63, washer 69a, washer 69, inner bearing 68, bearings 62 and drive sleeve 54, which force is applied through an annular flange 80 of sleeve 54 to a pair of parallel surfaces 81, 82 of the throw block 48. The drive sleeve 54 includes a reduced cylindrical extension 83 which extends between the trunnion 50 and the surfaces 81, 82 to give the drive sleeve 54 additional support and prevent rotation of drive sleeve 54- on trunnion 50.

Gear 64 meshes with a gear 85 which is rotatably mounted in idler bracket 67 by means of bearings 86 which engage a shaft 87 of gear 85. Gear 85 makes one revolution for each revolution of the throw block 48. Because the gear 58 is eccentric and must remain meshed with circular gear 60, the distance between the axes of trunnion 50 and the pin 61 varies throughout the cycle of throw block 48, as shown in FIG. 5. This variation is obtained by the engagement of the rack with the eccentric surface 59 through the bearings 56. Advantageously, gear 85 is coupled to the gear 60 by means of a universal coupling which permits relative movement between the axes of gears 85, 60 while closely maintaining the rotational relationship of gears 85, 60. This universal coupling is operatively connected to the gear 60 through a bevel gear train which defines a means for modifying the relative rotational relationship between gears 85, 60 and thus modifying the position of eccentric gear 53 and its integral eccentric surface 59 relative to trunnion 50 to thereby achieve a fine adjustment of the stroke of rack 35, which modifying means will be subsequently described in detail.

Gear 85 and the idler bracket 67 are permitted to reciprocate relative to rack 35 while they are prevented from rotating thereto by means or" a pin 83 which slidably engages a pair of parallel blocks 89. The pin 88 is rotatably mounted on bracket 67 and the blocks 89 are secured to rack 35 in parallel, spaced relationship as best seen in FIGS. 6 and 7. The previously mentioned universal coupling is an Oldham coupling which includes a cylindrical projection 90 extending axially from the gear 85 and axially aligned therewith and having a diametrically extending, rectangularly cross sectioned slot 91 therein. The Oldham coupling also includes a slide member 93 and a rotary member 95 slidably engaging a engaging a rectangularly cross sectioned diametrically extending projection 96 on slide member 93 by means of a slot 97. The slide member 93 is generally cylindrical and includes a diametrically extending rectangularly cross sectioned projection 98 disposed at 90 relative to projection 96 and positioned on the opposite surface therefrom, the projection 96 engaging slot 91.

The rotary member 95 is rotatably mounted on a bracket or frame 100 by means of a pair of bearings 101 secured to frame 100 which engage a reduced cylindrical portion 102 of member 95 and a suitable retainer ring 103 which engages portion 102 and bearings 101. The bracket 100 is mounted on rack 35 by means of bolts 104, shown in dotted line in FIG. 2. The rotary member 95 has an integral gear 106 which drives a bevel gear train mounted on the frame 100 in a manner which will be subsequently described.

The bevel gear train includes a first bevel gear 107 formed integrally with a cylindrical gear 106 and rotatably mounted on the pin 61 and engages a second bevel gear 110, rotatably mounted on a shaft 111 by means of a suitable bearing retainer 112 and bearings 113 and 115. Shaft 111 is pivotally mounted on pin 61. The pivotal position of shaft 111 is controlled by rotation of hand wheel 36 and its operatively connected square rod 46 in a manner which will be described. As long as wheel 36 and rod 46 are stationary, the position of the bevel gear remains unchanged and the rate of rotation between gears 58 and 64 remains unchanged. Under these conditions, gears 107 and 106 always makes one revolution for each revolution of the gear 64. A third bevel gear 114 is mounted on pin 61 and connected in driven relationship to the bevel gear 110. The bevel gears 107, 110 and 1-14 are each provided with a suitable mounting bearing 115. Bevel gear 110 acts as an idler and makes one revolution for each revolution of the throw block 48 unless the plane of bevel gear 110 is changed. If the plane of bevel gear 110 is changed, it either advances or retracts the rest of the train including the driven eccentric gear 58. The third bevel gear 114 is formed integrally with the circular gear 60 which meshes with eccentric gear 58. A first bearing separates bevel gear 114 from rack 35. Similarly a second bearing 120 separates bevel gear 107 from the frame 100.

The means for pivotally moving the bevel gear 110 relative to the pin 61 is best seen in FIGS. 2 and 6. As therein depicted, a screw 122 is rotatably mounted in frame 100 by bearings 123, and 124, and is operatively connected to square rod 46. A slide member 125 threadably engages screw 122 and includes an extension or arm 126 which slidably engages a pin 127 in frame 100 to prevent member 125 from rotating. When screw 122 rotates, slide 125 moves upwardly or downwardly, as viewed in FIGS. 2 and 6, depending on the direction of screw rotation. The slide 125 is operatively connected by means of a pin 128, a link 130 and a pin 131 to an arm 132 secured to shaft 111. Thus, rotation of handwheel 36 changes the pivotal position of shaft 111 and thereby advances or retards the eccentric gear 58 and eccentric surface 59 to define a fine adjustment of the crank arm of rack 35.

This fine adjustment of the stroke of rack 35 is achieved through the rotation of eccentric surface 59 relative to the rack 35 which rotation is accomplished through the bevel gear train and Oldham coupling, previously described, and this adjustment is achieved by rotation of the square rod 46. The details of the operation of the variable stroke adjustment can best be described with reference to FIG. 5 which is a view in elevation, partly in section and partly broken away, taken along the lines 5--5 of FIG. 2 and looking in the direction of the arrows and showing, in full lines, the terminal downward portion of rack 35 and showing in dotted outline various positions of the eccentric surface 59 and the throw block 48. These positions of the eccentric member 55 correspond to positions which the member 55 will have during the rotation of one cycle of the throw block 48. Because all of the gears are provided with suitable bearings and because the eccentric member 55 is journalled in suitable bearings, it is possible to quickly and easily pivot the shaft 111 of bevel 110 relative to the pin 61. When the shaft 111 pivots, bevel gear 110 acts as a lever connecting gears 107 and 114 with a force applied intermediate the level by shaft 111 and with the gear 107 acting as a fulcrum. Thus an upward force on the arm 132 produces a downward force on shaft 111 and gear 114. This force produces a corresponding rotation in eccentric surface 59 and a proportionate change in the stroke of rack 35, also termed a stroke arm.

Because the manual adjustment of the handle 36 of FIG. 1 produces a proportional rotation of the square rod 46 and this rotation produces a substantially proportional pivotal movement of the shaft 111 of bevel gear 110 and because the eccentric member 55 constitutes a pair of eccentric circles, the change in stroke will always be a substantially linear function of the angular rotation of the handvvheel 36. Thus, for example, With eccentric surface 59 having an eccentricity of As', the stroke of the rack 35 may be varied over a total micro-adjustment range of A". In this particular embodiment, the gear 58 may be rotated through a radial distance of 90 such that the angular range of displacement or change of the vstroke of the rack 35 Will change A. Further, as previously explained, because of the bearing mounting of all the gears in the gear train, it is possible to change the position of the bevel gear 110 while the mechanism is stationary, or it may be changed while the mechanism is in operation feeding strips. Still another advantage of this mechanism is that there is no backlash gearing and everything remains locked so that there is no looseness from one stroke to another. a

While we have shown and described one illustrative embodiment of this invention, it is understood that the concepts thereof may be employed in other embodiments without departing from the spirit and scope of this invention.

What we claim is:

1. In a drive stroke adjusting device for varying the stroke of a drive arm, the combination comprising:

7 a rotary shaft;

a throw block secured to said shaft;

a T-bolt adjustably mounted in said throw block;

a gear secured to said T-bolt;

a universal coupling operatively connected to said gear;

a bevel gear operatively connected to said universal coupling;

a first shaft rotatably mounting said bevel gear;

a second shaft pivotally mounted on said first shaft;

vmeans for pivoting said second shaft;

.a second bevel gear mounted on said second shaft;

.a third bevel gear rotatably mounted on said first shaft, said bevel gears being drivingly connected together;

.an eccentric member rotatably mounted on said T-bolt;

and

gear means operatively connecting said third bevel gear to said eccentric member, said eccentric member being rotatably mounted on said drive arm, whereby rotation of the second shaft changes the position of the eccentric relative to the T -bolt and thus changes the length of the stroke of the drive cam.

2. In a drive stroke adjusting device for controlling a predetermined longitudinal stroke of a drive arm, the combination comprising:

a crank arm; a

a trunnion mounted on said crank arm;

an eccentric rotatably mounted on said trunnion;

a drive gear secured to said trunnion;

a drive arm rotatably connected to said eccentric;

a bevel gear train including a shaft mounted on said drive arm, a first bevel gear rotatably mounted on said shaft, a second shaft pivotally mounted on'said first shaft, a second bevel gear rotatably'mounted on said second shaft, and a third bevel gear rotatably mounted on said first shaft;

a universal coupling for operatively connecting said drive gear to said bevel gear train;

gear means operatively connecting said bevel gear train to said eccentric; and

means for radially positioning said second shaft relative to said first shaft.

3. The combination according to claim 2 wherein said crank arm is a throw block including means coupling said trunnion to said crankarm in sliding relationship to define a coarse adjustment of the drive arm stroke.

4. The combination according to claim 2 wherein said means for pivoting said second shaft relative to said first shaft includes an operable crank, and means slidably and operatively connecting said operable crank to said second shaft.

5. In a 'drive stroke adjusting device of the character described, the combination comprising:

a trunnion;

a bevel gear train;

a universal coupling, operatively connecting said bevel gear train to said trunnion;

an eccentric rotatably mounted on said trunnion;

drive means rotatably mounted on said eccentric;

gear means operatively connecting said bevel gear train to said eccentric; and

means for pivoting one gear of said bevel gear train to change the relative position of said eccentric relative to said trunnion.

6. In a drive stroke adjusting device of the character described, the combination comprising:

a drive shaft;

a crank arm mounted on said drive shaft;

0. trunnion coupled to said crank arm;

an eccentric rotatably mounted on said trunnion;

drive means rotatably mounted on said eccentric;

a bevel gear train mounted on said drive means;

gear means operatively connecting said bevel gear train to said eccentric;

universal coupling means operatively connecting said trunnion to said bevel gear train; and means for pivoting one gear of said bevel train to change the position of said eccentric relative to said trunnion.

7. The combination according to claim 6, wherein said one bevel gear is rotatably mounted on a shaft which shaft is pivotally mounted on said drive means, and wherein said means for moving said one gear comprises an arm coupled to said last pivotally mounted shaft for pivoting said shaft, whereby the degree of said pivoting of said shaft is related substantially linear to the degree of rotation of said eccentric relative to said trunnion.

3. The combination according to claim 5, wherein said combination includes a drive sleeve mounted on said trunnion and wherein said eccentric is rotatably mounted on said drive sleeve, said eccentric including a pair of eccentric cylindrical surfaces whereby the stroke of the drive means varies substantially linear with the degree of rotation of said eccentric.

9. A drive stroke adjusting device for adjusting the stroke of a drive means comprising:

a trunnion;

an eccentric rotatable mounted on said trunnion;

drive means coupled to said eccentric;

bevel gear means mounted on said drive means for operatively connecting said trunnion to said eccentric; and

means for positioning one of said bevel gearmeans relative to said drive means whereby the stroke of said drive means is modified.

10. The combination according to claim 9 wherein said eccentric comprises a cylindrical member having a cylindrical surface for rotatably coupling said eccentric to said trunnion whereby the changes in the stroke of said drive means vary substantially linear with the degree of rotation of said eccentric.

11. The combination according to claim lt) wherein "longitudinal stroke of a reciprocating drive meansythe combination comprising:

a trunnion; an eccentric rotatably mounted on saidtrunnion;

a drive means operatively connected to said eccentric;

bevel gear means mounted on said drive means and operatively connected to said eccentric;

a coupling means operatively connecting said trunnion to said bevel gear means; and

means for positioning one of said bevel gear means relative to said drive means for varying the stroke of said drive means.

14. The combination according to claim 13 wherein said eccentric comprises a cylindrical member having an eccentric cylindrical passage therethrough whereby the changes in the stroke of said drive means vary substantially linear with the changes in rotation of said eccentric.

15. The combination according to claim 14 wherein said bevel gear means includes a gear shaft pivotally mounted on said drive means, and wherein said means for positioning one of said bevel gear means includes means for adjusting the position of said gear shaft relative to said drive means whereby said eccentric is rotated relative to said trunnion, the degree of eccentric rotation being directly proportional to the amount of gear shaft pivotal movement.

16. A drive stroke adjusting device for adjusting the throw of a drive means comprising;

a main drive shaft;

a throw block secured to said main drive shaft;

a trunnion mounted on said throw block;

a gear secured to said trunnion;

an idler bracket rotatably mounted on said trunnion;

eccentric gear means rotatably mounted on said trunnion and having an eccentric surface depending therefrom;

drive means rotatably mounted on said eccentric surface;

coupling means slidably operatively connected to said drive means to said idler bracket;

an idler gear rotatably mounted on said idler bracket and operatively connected to said first mentioned gear;

a gear rotatably mounted on said drive means;

a coupling means operatively connected between said idler gear and said last mentioned gear;

first bevel gear means including a gear operatively connected to said gear which is rotatably mounted on said drive means;

second bevel gear means including a bevel gear and means pivotally mounting said bevel gear relative to said first bevel gear means;

third bevel gear means operatively connected to said second bevel gear means to said eccentric gear whereby pivotal movement of said second bevel gear means is accompanied by proportionate changes in position of said eccentric surface.

17. A drive stroke adjusting device for adjusting the stroke of a drive means comprising:

a main drive shaft;

a throw block secured to said main drive shaft;

a trunnion mounted on said throw block;

a gear secured to said trunnion;

an idler bracket rotatably mounted on said trunnion;

eccentric gear means rotatably mounted on said trunnion and having an eccentric surface depending therefrom;

drive means rotatably mounted on said eccentric surface;

coupling means slidably coupling said idler bracket to said drive means;

an idler gear rotatably mounted on said idler bracket and meshing with said first mentioned gear;

a gear rotatably mounted on said drive means;

a coupling means coupled between said drive means mounted gear and said idler gear;

a first bevel gear rotatably mounted on said drive means and coupled in driven relationship to said coupling means;

a first shaft rotatably supporting said first bevel gear;

a second shaft pivotally mounted on said first shaft;

a second bevel gear rotatably mounted on said second shaft and meshing with said first bevel gear;

a third bevel gear mounted on said first shaft and meshing with said second bevel gear;

means coupling said third bevel gear to said eccentric gear; and

means coupled to said second shaft for pivoting said second shaft relative to said first shaft whereby the position of said eccentric gear relative to said trunnion is changed.

18. The combination according to claim 17 wherein said means for pivoting said second shaft relative to said first shaft includes a screw rotatably mounted in said drive means, means for rotating said screw, slide means threadably engaging said screw, an arm depending from said second shaft; and, link means coupling said slide means to said arm.

References Cited by the Examiner UNITED STATES PATENTS 2,856,793 10/1958 Budlong 74600 3,090,250 5/1963 Budlong 7460O BROUGHTON G. DURHAM, Primary Examiner,

W. S. RATLIFF, Assistant Examiner. 

1. IN A DRIVE STROKE ADJUSTING DEVICE FOR VARYING THE STROKE OF A DRIVE ARM, THE COMBINATION COMPRISING: A ROTARY SHAFT; A THROW BLOCK SECURED TO SAID SHAFT; A T-BOLT ADJUSTABLY MOUNTED IN SAID THROW BLOCK; A GEAR SECURED TO SAID T-BOLT; A UNIVERSAL COUPLING OPERATIVELY CONNECTED TO SAID GEAR; A BEVEL GEAR OPERATIVELY CONNECTED TO SAID UNIVERSAL COUPLING; A FIRST SHAFT ROTATABLY MOUNTING SAID BEVEL GEAR; A SECOND SHAFT PIVOTALLY MOUNTED ON SAID FIRST SHAFT; MEANS FOR PIVOTING SAID SECOND SHAFT; A SECOND BEVEL GEAR MOUNTED ON SAID SECOND SHAFT; A THIRD BEVEL GEAR ROTATABLY MOUNTED ON SAID FIRST SHAFT, SAID BEVEL GEARS BEING DRIVINGLY CONNECTED TOGETHER; AN ECCENTRIC MEMBER ROTATABLY MOUNTED ON SAID T-BOLT; AND GEAR MEANS OPERATIVELY CONNECTING SAID THIRD BEVEL GEAR TO SAID ECCENTRIC MEMBER, SAID ECCENTRIC MEMBER BEING ROTATABLY MOUNTED ON SAID DRIVE ARM, WHEREBY ROTATION OF THE SECOND SHAFT CHANGES THE POSITION OF THE ECCENTRIC RELATIVE TO THE T-BOLT AND THUS CHANGES THE LENGTH OF THE STROKE OF THE DRIVE CAM. 